Power transmission



June 16, 1953 J. B. BLACK ET AL POWER TRANSMISSION 4 Sheets-Sheet l Filed July 20, 1950 June 16, 1953 J. B. BLACK ETAL f 2,642,168

POWER TRANSMISSION Filed July 20, 1950 4 Sheets-Sheet 2 June 16, 1953 J. B. BLACK ETAL 2,642,168

POWER TRANSMISSION 95 fu e y J. B. BLACK ETAL POWER TRANSMISSION June 16, 1953 4 Sheets-Sheet 4 Filed July 20, 1950 KwJQQU Saul QN QN uay'a/ Patented June 16, 1953 UNITED smi S PATENT GFFIC,

POWERr TRANSMISSION Application July 20, 1950, Serial No. 175,034

15 Claims.

Our invention relates t power transmissions and more particularly to a unit for conveying power to a sliding gear transmission whereinv provision is made for hydraulically transmitting power to the load during the starting and accelerating period and for direct transmission when the load reaches a desired speed in conjunction with the ability to effect a full power shift from one drive to the other in either direction.

In units of this type, selectively controlled, hydraulically operated clutches are employed to determine hydraulic or direct drive to the gear transmission and where the latter does not include a synchronizing mechanism, it is desirable to reduce as far as possible the inertia ofthe parts aft of the clutches when disengaged for the purpose of facilitating gear shifting.

It is therefore the principal object of our invention to provide a transmission of the character indicated 4which embodies means for applying a substantial braking action on a device between the clutches and gear transmission during the period of clutch disengagement to thereby reduce the ywheel eiect of such device.

A further object is to devise a power transmission in which the hydraulic and direct drive clutches are positioned aft of the hydraulic power' transmitting partV of the unit, such as a hydraulic torque converter, with the parts arranged to provide only a single element, common to bothv clutches, that tends te exercise a flywheel eiTect on the gear transmission whenv the clutches are disengaged and which element is substantially braked to reduce such eiiect to a minimum.

A further object is to provide a transmission having a hydraulic system including the hydraulic torque converter, a pair of hydraulically operated clutches, a control valve for ldeterniining the actuation of the clutches and a pair of pumps for establishing pressure in the converter and working pressure for the clutches, one pump being engine driven and the other pump being driven by the single element with its output blocked under a determined relief when the Valve occupies neutral position.

A further object is to provide a transmission which utilizes leakage flow of the working liquid to lubrioate and cool the clutch plates.

These and further objects of the invention will be set forth in the following specification, reference being had to the accompanying drawings, and the novel means by which said objects are eiectuated will be definitely pointed out in the claims.

In the drawings:

(Cl. Biz-3.2)

Fig. 1 is a fragmentary, sectional elevation of the transmission as taken along the irregular line I--I in Fig. 2, the clutches being shown in disengaged position. v

Fig. 2 is an end view looking in the direction of the arrow 2 in Fig. l.

Fig- 3 isan enlarged sectional eleva-tion of a part of the transmission including the hydraulic drive clutch, the dump valve therefor and the control valve for determining the actuation of both clutches, the valve being shown in neutral position and indicating the relation thereof to certain passages communicating with a pipe leading to the hydraulic drive clutch.

Fig. 4 is a View similar to Fig. 3, omitting the clutch, showing the relation of the valve to certain other passages communicating with another pipe leading to the direct drive clutch.

Fig. 5 is a plan view of the control valve looking in the direction of the arrow 5 in Fig. 3 and showing the opposed relation thereto of the delivery pipes from the engine and output'shaft driven pumps.

Fig. 6 is a schematic layout of the hydraulic system, including as one circuit the clutches, the two pumps and control valve, and as another circuit the hydraulictorque converter and connected cooler, the clutches being disengaged.

Referring to Fig, 1, the numeral Iii designates a'driving ring that may be secured to an engine ywheel (not shown) or generally any power source and which has toothed, driving connection with a spider ring II having a hub I2 ywhich is journaled in the forward end wall I3 of a transmission housing Ill and is splined to one end of an input or driving shaft I5 that always rotates lat engine speed and extends within the housing.

Also journaled in the wall I3 and splined to the same end of the shaft I5 adjacent the hub I2 is a hub IG which carries an impeller Il forming part of a hydraulic torque converter I8. The outlet and inlet ends of the impeller Il are operably related, respectively, to connected turbines I9 and 20 constituting first and second stages of the converter, the turbine 20 having a hub 2| which is splined to a sleeve 22 that surrounds and extends for the major part of the length of the shaft I5 and is spaced therefrom to dene. an elongated, annular chamber 23 for a purpose presently explained. The `forward end of the sleeve 22 is journaled in a bearing 24 mounted within the impeller hub IS and another part of the sleeve is journaled: in a bearing 25 mounted in an intermediate housing wall 26.

A reaction member 21 is located between the turbines I9 and 26 and functions in the characteristic manner with respect thereto when power is transmitted through the converter. The hub of the member 21 is keyed to a ring 28 that is journaled on spaced bearings 29 and 29a carried by a cylindrical extension 30 attached to the central part of the wall 26, the extension being spaced from the sleeve 22 to create an annular passage 3| whose forward end communicates through one or more ports 32 in the turbine hub 2| with the interior of the converter I8 and whose rear end just forwardly of the bearing 25 communicates through a radial passage 33 in the sleeve 22 with the chamber 23, all for a purpose presently explained. Interposed between the ring 28 and extension 36 is a freewheel or overrunning clutch 34 of usual construction which is arranged to hold the reaction member 21 stationary during power transmission through the converter and to permit it to rotate freely with the impeller I1 and turbines I9 and 20 during direct drive.

Substantial losses of working liquid from the ends of the converter I8 are prevented by forward and rear annular cover plates 35 and 36 Whose outer peripheries are connected to the turbine I9 and whose inner peripheries t against piston ring seals 31 and 38 carried by the impeller hub I6 and the wall 26, all respectively. Similar loss at the central portion of the converter is prevented by a piston ring seal 39 interposed radially between the impeller hub I6 and sleeve 22 and axially between the turbine hub 2 I and bearing 24.

An annular carrier 49 is splined to the sleeve 22 rearwardly of the wall 26 and its right face, as viewed in Fig. l, is, recessed to provide outer and inner concentric annular cylinders 4I and 42. The carrier forms the closed ends of the cylinders and extending from the carrier beyond the open ends of and between the cylinders is an externally and internally splined or toothed annulus 43.

An annular piston 44 is slidably mounted in the cylinder 4| in actuating relation to a plurality of clutch plates 45, alternate plates having toothed and sliding engagement-l with the outer splined surface of the annulus 43 while the intervening plates are similarly engaged with a shell 46 formed integrally with an annular spider 41 having a hub 48 that is keyed to one end of an output shalt 49 which, it will be assumed, is connected to the input shaft of a sliding gear transmission (not shown). The plates 45 are engaged bythe piston 44 against an abutment ring 50 whose central portion is secured to the annulus 43. The piston 44, plates 45 and the outer portion of the ring 50 constitute the hydraulic drive clutch of the transmission which, when engaged., establishes drive through the converter I8, sleeve 22, carrier 46, and clutch plates 45 to the spider 41. When the actuating pressure on the piston 44 is removed, release of the clutch plates 45 is effected by a plurality of helical springs I that respectively abut a ring 52 mounted on the outer periphery of the piston 44 and an abutment ring 53 mounted on the carrier 40, the ring 52 abutting the carrier when the springs are fully extended. The spider hub 46 is `iournaled within a bearing 54 interposed therebetween and the rear end wall 55 of the housing I4 through which the shaft 49 extends.

An annular piston 56 is slidable in the cylinder 42 and is operably related to a plurality of clutch plates 51, alternate plates having` toothed and sliding engagement with the inner splined surface of the annulus 43 while the intervening plates have similar engagement with a toothed shell 58 CTI formed integrally with a hub 59 splined to the rear end of the driving shaft I5. The hub 59 is journaled within a bearing 6I] interposed therebetween and the spider hub 48. The plates 51 are engaged by the piston 56 against the inner portion of the abutment ring 59 and release of these plates is effected by a plurality of helical springs 6| whose opposite ends respectively abut the piston 56 and ring 62 which ts on the sleeve 22 and is suitably held against axial movement. The piston 56, plates 51 and the inner portion of the abutment ring 59 form the direct drive clutch of the transmission.

Selective hydraulic actuation of the hydraulic and direct drive clutches and the maintenance of 'a working pressurev in the converter are accomplished by the following instrumentalities (see Figs. 1, 2 and 6).

An engine driven pump 63 withdraws oil through a pipe 64 from a sump 65 which is preferably remote from the lower part of the housing I4 and is connected to the latter by a pipe 66 whereby oil collected in the housing as presently described drains to the sump. The delivery side of the pump 63 connects by a pipe 61 with one side of a control valve 68 and bridged around the pump 63 is a pair of series related, pressure regulating valves for determining the pressure of the actuating oil for the clutches and the pressure of the oil in the converter circuit.

Specically, and referring to Fig. 6, a pipe 69 connects the delivery pipe 61 with the inlet of a pressure regulating valve 10 whose outlet connects by a pipe 1| with the inlet of a pressure regulating valve 12 Whose outlet connects by a pipe 13 with the pipe 64 and hence with the sump 65. By way of example, the valve 18 is set to open at p. s. i. while the valve 12 is set to open at 50 p. s. i., these valves being conventional in operation. Due to the manner in which these valves are coupled together, the valve 12 back pressures the valve 10 so that a pressure of 150 p. s. i. is available in the delivery pipe 61, but only 50 p. s. i. is present in the pipe 1I Specifically'y this result is obtained by making the pressure in the pipe 1| effective against the spring actuated side of the valve 10 so that opening of this valve is against the combined pressures of its spring |35 and the pipe 1| pressure as determined by the valve 12, the latter being made effective, for example, by connecting the right end of the valve 16 (see Fig. 6) by a pipe |36 to a pipe 14 which communicates with the pipe 1|.

The pipe 1I communicates by way of the pipe 14 with one end of a pipe 15 constituting the inlet to the converter I8 (see Figs. 1, 2 and 6) and the opposite end of the pipe 15 is mounted in the central portion of the wall 26 and communicates through a passage 16 with the annular passage 3| and thence through the ports 32 with the inner part of the converter circuit. The converter discharges just interiorly of the cover plate 36 and outwardly of the reaction member 21 into a spaceV 11 which in turn connects with a passage 18, also in the central part of the wall 26, and thence with one end of a pipe 19 which serves as the outlet from the converter circuit. It will be understood that the vpipes 15 and 19 are spaced from each other transversely of the transmission and that the passages 16 and 18 are similarly related. The pipe 19 feeds oil from the converter I 8 to the inlet of a cooler 8D and the outlet of the latter connects by a pipe 8| with the pipe 15. Circulation in the converter cooler circuit is effected by the normal pressure available in the converter I8 and is not due to the pump 63 which through the vregulating valves 'I0 and `'I2 merely serves to maintain a basic pressure in the converter cooler circuit,` assumed in the present instance to be 50 D. s. i. f

A second pump .82 is also provided for the transmission and is driven by a shaft 83 (see Fig. 1) `which is drivingly connected to -a gear84 whose hub is journaled in the end wal1'55 and which meshes with a pinion 85 formed integrally with the hub 48. The pump 82 can therefore be driven from the output shaft 49 whenever both clutches are disengaged and it is necessary to push the tractor to start the engine, the sliding gear transmission being engaged in one of its speeds. Under theserconditions, the pump 82 furnishes pres- 'sure tov engage both clutches as will be presentlg7 described. y

f The suction side of the pump l82 connects lby-a pipe 86 with the-pipe 64 and hence with the sump S5 while Athe delivery side connects by a pipe El With-the control valve 68 in generally opposed relation to the connection of the pipe 61 therewith, i. e., the deliveries from the pipes 61 and 8l are-masked by the control valve 18 when in neutral position. A pressure regulating valve 88a s bridged around the pump S2 and is adjusted to a pressure of or above 150 p. s. i. for a reason presently explained.

Referring to Figs. 3, 4 and 5 which show the details of the control valve 63, the latter includes a casing 83 mounted on the housing I4 and having an elongated here 89. Slidable in the bore 8S 'isa valve stem 9B whose right end (see Fig. 6) is connected to a pivoted actuating handle QI whereby the stem may be reciprocated in the bore. For the purpose of holding V,the stern 9|! in any selected position, it includes annular grooves 92, 93 and 95 spaced axially thereof and arranged to selectively engage a spring actuated detent 85 (see Fig. 2), the grooves respectively determining valve sternA positions corresponding to neutral, hydraulic and direct drive conditions of the transmission. l

v- The 'valve stem Si! further includes piston valves et and el which closely lit the bore 89 and are spaced axially by a reduced vneck 93. Annuler ports Se and Idil surround the bore -89 on opposite sides of the piston '91 when the stem 9G occupies the Vneutral position shown in Fig. 3 and respectively communicate with chambers I lli and |82 in the casing S8 (see Figs.- 3 and 4) which are displaced from each other `transversely of the casing. Annular ports |33 and itil also surround the bore 8%, the former, when the stem 9G is in the position shown in Fig. 3, being positioned just to the leftY of the piston valve 96 and the latter to the left of the port |99, the ports |93 and |64 communicating, respectively, through aligned passages in the casing 83 and the top wall of the-housing Ill generally designated vas exhaust passages |05 and |96. Any oil that flows through the latter passages collects in the bottom ofthe housing It and is returned to the sump '65 through the pipe 65.

The outer end of apipe |01 extends through the top wall 'of the housing I4 in communication with the chamber IUI while the inner `end Vis mounted in a ring |68 (see Fig. 1) secured to the central part of the housing wall and in encircling and sealed relation to a hub I 09 formed integral with the carrier 40. The inner end of thefpipe lill communicates through a chamber IIEI provided in the ring |08 and an annular channelA -I II vformed in lthe outer surface of the hub |09 with one lor more longitudinal passages I I2, also provided in the hub |09, the left end of each passage IIZ being closed by a plug I|3.

he opposite end of the passage or passages H2, as the case maybe, connects with the inner end of one or more radial passages IIl provided in the carrier 4t. For simplificationgonly one passage ||2 land one passage H4 are illustrated.

Oil flowing through the passage ile supplies actuating pressure to the hydraulic drive cylinder 4| and control 0f this flow is exercised by a ydump valve ||5, there being one such valve for each passage H4. Referring to Fig. 3, the dump valve H5 includes a casing IIB which may be integral with or attached to the carrier 40 adjacent the periphery thereof and offset circumferentially of the carrier so as to clear the passage II, the lower end of the casing H6 being closed by a wall ill and its bore Il being open at its outer end. Closing the outer end of the casing ||6 is a cover IIS having a chamber v52|) whose ends constantly communicate respectively with the outer end of the passage Illi and the outer end of the bore IIS. Y

Slidable in the bore I I8 is a piston valve |2| whose movements outwardly are limited by bosses |22 for abutting the cover H9 and inwardly by a reduced extension |23 for abutting the wall `I The piston valve |25 is shown in dumping position in Fig. 3 in which it occupies its outermost position and sufficiently uncovers a port |24 providing communication between the cylinder 4| and bore H3 and thence around `the extension |23 through a port |25 inthe casing IIS connecting the bore H8 with the interior of the housing Ibi and hence with the-sump 65. A third port |26 in the casing Ii 5 at the inner end thereof provides exhaust for any oil that may leak past the guide shoulder |27 provided kon the inner end of the extension |23. When pump pressure is effective in the passage Hi, it shifts the piston valve |v2| inward, or downward as viewed in Fig. 3, to thereby mask the exhaust port |25 and uncover the port IM w-hich is thereby placed in communication with the chamber |26 so that pressure is supplied to the hydraulic drive cylinder di.

YThe dump valve operates on the principle of pump pressure shifting the piston valve -IZI inwardly to thereby engage the hydraulic drive clutch, but when pump pressure to this clutch interrupted, then at any speed of the' engine, the centrifugal force due to the weight of the piston valve |2| is greater than that due to the weight of the column of oil in the passage IIe. Under the latter conditions, therefore, the valve Vshifts outwardly to the quick dumping position shown in Fig. 3 whereupon the springs 5i release the hydraulic drive clutch. Due to the smaller radius of the direct drive clutch, dump valves :are not necessary therefor since therelease springs IBI effectively counteract the .centrifugal action yon the relatively small masses of -oil en route to the cylinder for this clutch vwhen the pump pressure i's interrupted.

` The passages throughwhich oil is transferred from the control valve 6E to the direct drive cylinder d'2 will now be described. Referring to Figs. 1 and4, the outer end of' a `pipe |23 extends through the top wall of the housing I4 in ccmmunication with the chamber |62, the pipe |28 being spaced from the Apipe It? transverselyof the transmission and the inner end is mounted in the ring |98 in communication with a chamberl29, also included in the ring M38. The

chamber |29 connects with an annular channel provided in the outer surface of the carrier hub |09 and this channel in turn connects with one or more longitudinal passages |3| in the hub |09 that communicate with the direct drive cylinder 42.

In describing the operation of the transmission, it will be assumed that the vehicle or tractor is at rest with the engine idling, thus driving the impeller I1 and the pump 63, and that the valve stem 90 is in the neutral position shown in Fig. 3. The piston valve 91 then masks the delivery ends of the pipes 61 and 81 leading from the engine and output shaft driven pumps 63 and 82, respectively, although the latter pump is not then operating. Pump pressure is therefore denied to the outer ends of the pipes |01 and |28 and hence to the hydraulic and direct drive clutch cylinders 4| and 42. At the same time, the pipe |01 connects with the sump 65 through the chamber IOI, annular port 99, bore 89, annular port |03, passage |05, the housing I4 and the pipe 65, while the pipe |28 connects with the sump 95 through the chamber |02, annular port |00, bore 89, annular port |04, passage |06, the housing I4 and the pipe 60. Accordingly, the dump piston valve I2| occupies the position shown in Fig. 3 and both clutches are disengaged.

The operator then shifts the sliding gear transmission into rst speed and moves the valve stem 90 towards the left until the detent 95 engages the groove 93. The piston valve 90 then masks the annular port |03 and hence the exhaust passage |05 while the piston valve 91 uni.

covers the delivery ends of the pipes 51 and 81 so that oil under pressure from the pump B3 flows to the annular port 99 and thence through the pipe |01 and the connected passages and through the dump valve II5 to the clutch cylinder 4I to thereby engage the hydraulic drive clutch. At the same time, the piston valve 91 still denies pressure to the chamber |02 so that the direct drive clutch remains disengaged, the latter chamber remaining in communication with the sump B5.

With the hydraulic drive clutch engaged, the engine is connected to the output shaft 49 through the torque converter IEB, the reaction member 21 being held from rotating in reverse direction by the overrunning clutch 34 and the vehicle begins moving. When sucient acceleration of the vehicle has been accomplished to enable the selection of a higher speed ratio in the gear transmission, it is necessary to first disengage the hydraulic drive clutch by returning the valve stem to the position shown in Fig. 3 and thereafter make the gear shift in the usual way.

During this gear change, the inertia of the spider 41, through which the hydraulic drive clutch had been transmitting power to the output shaft 49, exerts a flywheel effect on this shaft that would tend to hamper an easy gear shift. It is an important feature of the invention that means are provided for retarding the rotation of the spider during this period of operation. Since the pump 82 is driven by the spider 41 and further since at the instant of gear shift, the delivery of this pump is blocked by the neutral position of the control valve 68 and all output ow thereof must pass through its regulating valve 08a, a definite torque drag is imposed on the spider 41 which slows the output shaft 49 sufficiently to facilitate gear shifting. A braking action of any desired degree can be accomplished by adjusting to the required amount the pressure in the relief circuit of the pump 82 so long as this pressure is not below that utilized for engaging the clutches. Whenever the control valve 68 is in positions other than neutral, the pump 82 merely delivers oil to the hydraulic system under the regulation provided by the valves 10 and 12.

The foregoing operation is repeated through all the gear changes in the gear transmission up to and normally including high gear, the control valve 68 being reciprocated between neutral and hydraulic drive positions as above described with all power flow being transmitted through the converter I8. This mode of operation takes advantage of the high starting torque and capacity for rapid, smooth acceleration afforded by the converter I8.

When the vehicle is accelerated to the desired speed, it is desirable to provide direct drive between the engine and the load. This result is accomplished by further shifting the valve stem towards the left until the detent 95 seats in the groove 94. The piston valve 96 then occupies a position further to the left of the annular port |03 but short of the annular port 99 so that the hydraulic drive clutch is unaffected and remains engaged. The piston valve 91 however masks the annular exhaust port |04 and uncovers the port |00 so that pressure oil from the pumps 63 and 82 then ows through the pipe |28 and the connected passages described above to the direct drive cylinder 42 to thereby engage the associated clutch. The drive is then through the shaft I5, both clutches which are in series relation and the spider 41 to the output shaft 49.

Prior to this direct drive connection, the speed of the carrier 40 is less than that of the shaft l5 due to the usual loss through the converter, but when the direct drive clutch is engaged, the speeds of the carrier 40 and shaft I5 are equalized. Since the hydraulic drive clutch remains engaged, the impeller I1 and the turbines I9 and 20 rotate at the same or engine speed. Hence, there will not be any reaction against the blades of the reaction member 21 which, as it is released by the overrunning clutch 34, will begin to rotate with the impeller and turbines. Since power is not then being transmitted through the converter and all parts thereof are rotating at substantially the same speed, the power losses in the converter circuit are negligible. Actually, the reaction member 21 rotates at a slightly slower speed than the mpeller and turbines due to the drag of the bearings and the overrunning clutch, but the difference is small.

If the load becomes too heavy to be carried in direct drive, the valve stem 90 is shifted to the hydraulic drive position, i. e., with the detent 05 seating in the groove 93 to thereby deny pressure to the direct drive clutch Whose cylinder is connected to the sump by uncovering the port |00 and placing the same in communication with the exhaust port |04 while the hydraulic drive clutch remains engaged. The shift from hydraulic to direct drive and vice versa may be made at any speed ratio in the gear transmission, but when a shift is made in the transmission, both clutches must be disengaged by moving the control valve 68 to neutral position.

vA particular advantage of the above constructionl is that the transmission is characterized by a full power shift, the engine at no time being completely disconnected frorntheoutput shaft 49 while the changes-'from onev drive to the other is being eiected. As load conditions vary for' any given gear situation in the gear transmission, the drive through the transmission I4 may be shifted at will from hydraulic to direct and from direct to hydraulic with the hydraulic drive clutch being always engaged.

v A further feature of the invention in addition to the above and the location of 'the clutches aft of the converter I8 which makes possible aA single element connection between the clutches and the Output shaft 49, is the provision for lubricating and cooling the clutch plates.

Oil is tapped from the passage Sii and led through the port 3,3 into the annular' chamber E3 and to this quantity isadded the leakage past the seal 39 which flows through the bearing 24 and thence to the chamber 23. The oil thus collected iiows towards the right, as viewed in Fig. 1, and radially outward past the end of the sleeve 22 to an annular space 932 within the shell 58 which includes a plurality of apertures |33 through lwhich the oil flows to the inner peripheries of the clutch plates i. Radial pasm sages |34 are also provided in the annulus 43 through which oil thrown outwardlyby the plates 51 flows to thev clutch plates 45 and oil discharged by the latter collect in the bottom of the housing I4 for return to the sump.

We claim:

1. In a power transmission, the combination of a hydraulic power circuit means including an impeller arranged for connection to a power source and a turbine, a member adapted for connection to an output shaft, first hydraulically actuated clutch means for connecting the turbine to the member, second hydraulically actuated clutch means shiftable between positions providing and interrupting a direct drive between the source and member, ythe first and second clutch means.

being located aft of the turbine and the second clutch means when engaged driving through the first clutch means, `and a hydraulic pressure system including both clutch means and a control means, the control means being operable to dea hydraulic power circuit means including animpeller arranged for connection to a power source and a turbine, a member adapted for connection .being drivably connected to the member for providing hydraulic drive and other friction parts .of the inner clutch being drivably connected to the power source whereby the inner clutch provides direct drive through the outer clutch when member, and a hydraulic pressure system including the clutch means, a pump drivably connected to the member for establishing working pressure for the clutch means, pressure relief means for the pump, and a control valve for determining the actuation of the clutch means, the control valve in neutral position blocking delivery of the pump whereby rotation of the member is braked `at the instant of clutch means disengagement.

5. In a power transmission, the combination of a hydraulic power circuit means including an impeller arranged for connection to a power source and a turbine, a member adapted for conf nection to an output shaft, a carrier connected to an output shaft, a carrier connected to and located aft of the turbine, outer and inner. conf centric, friction clutches mounted on the carrier, friction parts of each clutch being drivably connected to the carrier, other friction parts of the outer clutch being drivably connected tothe member for providing hydraulic drive and other friction parts ofthe inner clutch being drivably connected to the power source whereby the,k inner clutch provides direct drive through the youter clutch when engaged to the member, and means for controlling the operation of both clutches.

3. In a power transmissiorrrthe combination of a hydraulic power circuit means including an impeller arranged for connection to a power source and a turbine, a member adapted for connection to an output shaft, a carrier connected to and located aft of the turbine, outer and inner, concentric and hydraulically actuated, friction clutches mounted on the carrier, friction parts of each clutch being drivably connected to the carrier, other friction parts of the outer clutch concentric and hydraulically actuated, friction clutches mounted on the carrier, friction parts of each clutch being drivably connected to the carrier, other friction parts of the outer clutch being drivably connected to the member for providing hydraulic drive and other friction parts of the inner clutch being drivably connected to the power source whereby the inner clutch provides direct drive through the outer clutch when engaged tothe member, and a hydraulic pressure system including both clutches, a pump drivably connected to the member for establishing working pressure for both clutches, pressure relief means for the pump, and a control valve, the valve being operable to determine the actuation of the outer clutch and selectively the engagement and disengagement of the inner clutch while the outer clutch is engaged and when in neutral position blocking delivery of the pump whereby rotation of the` member is braked at the instant both clutches are disengaged.

6. In a power transmission, the combination of a driving shaft connectible to a power source, a sleeve encircling the driving shaft, hydraulic power circuit means including an impellei connected to one end of the driving shaft and a turn bine keyed to an intermediate part of the sleeve, a disk member coaxial with the driving shaft and adapted for connection to an output shaft, a carrier connected to the sleeve andlocated aft of the turbine, outerand inner, concentric, friction clutches mounted on the carrier, friction parts of each clutch being drivably connected to the carrier, other friction parts of the outer clutch beingdrivably connected to the member for providing hydraulic drive and other friction parts of the inner clutch being drivably connected to the other end of the driving shaft wherebyV the inner clutch provides direct drive through the outer clutch when engaged to the member, and means for controlling the operation of both clutches.

7. In a power transmission, the combination of a driving shaft connectible to a power source, a sleeve encircling the driving shaft, hydraulic power circuit means including an impeller connected to one end of the driving shaft and a turbine keyed to an intermediate part of the sleeve, a disk member coaxial with the driving shaft and adapted for connection to an output shaft, a carrier connected to the sleeve and located aft of the turbine, outer and inner, concentric and hydraulically actuated, friction clutches mounted on the carrier, friction parts of each clutch being drivably connected to the carrier, other friction parts of the outer clutch being drivably connected to the member for providing hydraulic drive and other friction parts of the inner clutch being drivably connected to the other end of the driving shaft whereby the inner clutch provides direct drive through the outer clutch when engaged to the member, and a hydraulic pressure system including both clutches, a pump drivably connected to the member for establishing working pressure for both clutches, pressure relief means for the pump, and a control valve, the valve being operable to determine the actuation of the outer clutch and selectively the engagement and disengagement of the inner clutch while the outer clutch is engaged and when in neutral position blocking delivery of the pump whereby rotation of the member is braked at the instant both clutches are disengaged.

8. In a power transmission, the combination of a driving shaft connectible at one end to a power source, a sleeve encircling and spaced from the driving shaft to provide an annular chamber, hydraulic power circuit means including an impeller connected to said one end of the driving shaft and a turbine keyed to an intermediate part of the sleeve, a hub connected to the opposite end of the driving shaft, a disk member coaxial with the driving shaft and :adapted for connection to an output shaft, a carrier connected to the sleeve and located aft of the turbine and having an annulus projecting from one side thereof, outer and inner, concentric, friction clutches mounted on the carrier, friction parts of each clutch being drivably connected to the annulus, other friction parts of the outer clutch being drivably connected to the member for providing hydraulic drive and other friction parts of the inner clutch being drivably connected to the hub whereby the inner clutch provides direct drive through the outer clutch when engaged to the member, means for controlling the operation of the clutches, the annulus and hub each including a plurality of radial passages therethrough for respectively providing communication between the plates of the clutches and the chamber, and means for collecting working oil in the chamber for flow through the passages to lubricate and cool the clutch plates.

9. In a power transmission, the combination of a hydraulic power circuit means including an impeller arranged for connection to :a power source and a turbine, a disk member adapted for connection to an output shaft, hydraulically actuated clutch means located aft of the turbine and engageable to connect the turbine to the member, and a hydraulic pressure system including the clutch means, rst and second pumps respectively connected to the member and to the power source for establishing working pressure for the clutch means, pressure relief means for each pump, and a control valve for determining the actuation of the clutch means, the control l2 valve in neutral position blocking deliveries of the pumps whereby rotation of the member is braked bythe first pump at. the instant of clutch means disengagement.

l0. In a power transmission, the combination of a hydraulic power circuit means including an impeller arranged for connection to a power source and a turbine, a member adapted for connection to an output shaft, first hydraulically actuated clutch means for connecting the turbine to the member, second hydraulically actuated clutch means shiftable between positions providing and interrupting `a direct drive between the source and member, the first and second clutch means being located aft of the turbine and being series related for power ow from the second to the first clutch means during direct drive, and a hydraulic pressure system comprising both clutch means and a control valve opera-ble to determine the engagement of the first clutch means, to selectively determine the engagement and disengagement of the second clutch means, and to maintain the engagement of the first clutch means during the engagement ofthe second clutch means.

11. In a power transmission, the combination of a hydraulic power circuit means including an impeller arranged for connection to a power source and a turbine, a member adapted for connection to an output shaft, first hydraulically actuated clutch means for connecting the turbine to the member, second hydraulically actuated clutch means shiftable between positions providing and interrupting a direct drive between the source and member, the first and second clutch means being located aft of the turbine and being series related for power fiow from the second to the first clutch means during direct drive, and .a hydraulic pressure system comprising both clutch means, a pump drivably connected to the member for establishing working pressure for both clutch means, pressure relief means for the pump, and a control valve operable to determine the engagement of the first clutch means, to selectively determine the engagement and disengagement of the second clutch means, ,and to maintain the engagement of the first clutch means during the engagement of the second clutch means, the control valve in neutral position blocking delivery of the pump whereby rotation of the member is braked at the instant both clutch means are disengaged.

l2. In a power transmission, the combination ofa driving shaft connectible to .a power source, a sleeve encircling the driving shaft, hydraulic power circuit means including an impeller connected to one end of the driving shaft and a turbine keyedto an intermediate part of the sleeve, a disk member coaxial with the driving shaft and adapted for connection to an output shaft, a carrier connected to the sleeve and located aft of the turbine, outer and inner. concentric and hydraulically actuated, friction clutches mounted on the carrier, friction parts of each clutch being drivably connected to the carrier, other friction parts of the outer clutch being drivably connected to the member for providing hydraulic drive and other friction parts of the inner clutch being drivably connected to the other end of the driving shaft whereby the inner clutch provides direct drive through the outer clutch when engaged to the member, and a hydraulic pressure system including both clutches and a control valve, the valve being operable to determine the actuation of the outer clutch and selectively the engagepower flow through the circuit means to theA y 14 impeller arranged for connection to a power source `and a turbine, a member adapted for connection to an output shaft, a carrier connected member, and a hydraulic pressure system including the clutch means, a pump drivably connected to the member for establishing working pressure for the clutch means, pressure relief means for the pump', and a control valve for determining the actuation ofthe clutch means, `the control valve in neutral position blocking delivery of the pump whereby rotation of the member is braked at the instant of clutch means disengagement.

V14. In a power transmission, the combination of a hydraulic power circuit means including an impeller arranged for connection to a power source and a turbine, a disk member adapted for connection to an output shaft, hydraulically actuated clutch means engageable to establish .a

power flow through the circuit means to the member, and a hydraulic pressure system including the clutch means, first and second pumps respectively connected to the member and to the power source for establishing working pressure for the clutch means, pressure relief means for each pump, and a control valve for determining the actuation of the clutch means, the control Valve in neutral position blocking deliveries of the pumps whereby rotation of the member is braked by the iirst pump at the instant of clutch means disengagement.

15. In a power transmission, the combination of a hydraulic power circuit means including an to and located aft of the turbine, outer and inner, concentric and hydraulically actuated, friction clutches mounted on the carrier, friction parts of each clutch being drivably connected to the carrier, other friction parts of the outer clutch being drivably connected to the member for -providing Yhydraulic drive and other friction parts of the inner clutch being drivably connected to the power source whereby the inner clutch provides direct drive through the outer clutch when en gaged to the member, and a hydraulic pressure system including both clutches, first and second pumps respectively connected to the member and to the power source for establishing working pressure for both clutches, pressure relief means for each pump, and a control valve operable to determine the actuation of the outer clutch and selec'- tively the4 engagement and disengagement of the inner clutch while the outer clutch is engaged and when in neutral position blocking deliveries of the pumps whereby rotation of the member is braked Vby the rst pump at the instant both clutches are disengaged.

JAMES B. BLACK.

WILBUR F. SHURTS.

References cited inv the me of this patent UNITED STATES4 PATENTS Number y Name p Date 2,226,801 Black Dec. 31, 1940 2,235,418 Buchhart Mar. 18, 1941 2,289,019 Jessen July 7, 1942 2,449,586 Carnagua 1 Sept. 21, 1947 

